Variable speed power transmission

ABSTRACT

The present invention comprises: a drum assembly, connected to an input shaft from a suitable torque power source, having a cylindrical chamber carrying fluid, the chamber having fins at intervals on its inner cylindrical wall; a rotor connected to an output shaft, carried in the drum assembly, having a plate perpendicularly disposed to the rotor output shaft, and having a plurality of selectively movable blades disposed at intervals distally from the circumference of the rotor plate; and means for selectively changing the angular relationship of the blades with respect to the rotor plate.

United States Patent 1191 Allsup, Sr. 1 1 Aug. 7, 1973 [54] VARIABLESPEED POWER TRANSMISSION 126,484 1/1948 Australia 416/ 157 A [76]Inventor: John R. Ansup Sr" 203 Garfield 414,641 8/1934 Great Brltam192/58 A Ave., Yakima, Wash. 98902 Primary Examiner-Charles J. MyhreFlledi 20, 1971 Assistant ExaminerThomas C. Perry Attorney-John Kraft 52us. 01 74/720, 192/58 A,.416/l57 A [57] ABSTRACT [51] Int. Cl. Fl6h47/06, Fl6d 35/00 The present invention comprises: a drum assembly, [58]Field of Search 192/58 A; 74/720; connected to an input shaft from asuitable torque 416/157 A power source, having a cylindrical chambercarrying fluid, the chamber having fins at intervals on its inner [56]References Cited cylindrical wall; a rotor connected to an output shaft,

UNITED STATES PATENTS carried in the drum assembly, having a plateperpendic- 1 931 204 10/1933 Rudquist 192/58 A dispmd the Shaft andhaving a 2693l20 11/1954 Maybach 74,720 X plurality of selectivelymovable blades disposed at in- 5/1956 m- 416/157 A tervals distally fromthe circumference of the rotor 2,938,397 5/1960 Lemmetty 192/58 A Xplate; and means for selectively changing the angular 3,054,307 9/1962Burckhardt 74/720X relationship of the blades with respect to the rotorFOREIGN PATENTS OR APPLICATIONS Plate- 122,l44 4 Claims, 10 DrawingFigures 9/1946 Australia 416/157 A 'PATENIED 3. 750.493

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JQHN R. ALLSUF' SR.

VARIABLE SPEED POWER TRANSMISSION FIELD OF INVENTION The presentinvention relates to power transmissions and more particularly totransmissions operable to provide continuous variations throughout theoutput range.

DESCRIPTION OF THE PRIOR ART Power transmissions-commonly used andemployed, generally, comprise a variety of combinations of gears andhydraulic mechanisms. Commonly, transmissions provided with gears have,as a characteristic, peak efficiencies which may be described as pointson the power outputting range between which there are discontinuousjumps in the power, corresponding to changes to gear ratios.Characteristically, these changes in gear ratio have been provided bymeans of complex clutch devices. Gear transmissions in combination withhydraulic devices have similar characteristics of discontinuousvariations through the power transmission SUMMARY OF THE INVENTIONGenerally, the present invention comprises: a drum assembly, connectedto an input shaft from a suitable torque power source, having acylindrical chamber carrying fluid, the chamber having fins at intervalson its inner cylindrical wall; a rotor connected to an output shaft,carried in the drum assembly, having a plate perpendicularly disposed tothe rotor output shaft, and having a plurality of selectively movableblades disposed at intervals distally from the circumference of therotor plate; and means for selectively changing the angular relationshipof the blades with respect to the rotor plate.

A more thorough and comprehensive understanding may be had from thedetailed description of the preferred embodiment when read in connectionwith the drawings forming a part of this specification.

BRIEF DESCRIPTION OF THE DRAWINGS:

FIG. 1 is a side elevational view of the variable speed transmission ofthis invention showing the hydraulic torque converter and countergearassembly.

FIG. 2 is a cross-sectional view taken substantially along the lines 22of the FIG. 1 showing the gearset of the countergear assemblycommunicating with the driven pinion gear.

FIG. 3 is a cross-sectional side elevational view of the hydraulictorque converter of this invention drawn to a larger scale. I

FIG. 4 is a cross-sectional view of the hydraulic torque converter takensubstantially along the lines 44 of the FIG. 3.

FIG. 5 is a fragmentary cross-sectional view of the hydraulic torqueconverter taken substantially along the lines 55 of the FIG. 3.

FIG. 6 is a cross-sectional view of the hydraulic torque converter takensubstantially along the lines 6-6 of the FIG. 3.

FIG. 7 is a cross-sectional perspective view of the hy draulic torqueconverter taken substantially along the lines 77 of the FIG. 3, drawn toa larger scale.

FIG. 8 is a side elevational view of a further embodiment of thehydraulic torque converter of this invention.

FIG. 9 is a cross-sectional view of the hydraulic torque converter takensubstantially along the lines 9-9 of the FIG. 8.

FIG. 10 is a cross-sectional perspective view of the hydraulic torqueconverter taken substantially along the lines 10l0 of the FIG. 8.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT:

- Referring now to the drawings and more particularly to the FIG. 1, thevariable speed power transmission of the present invention is shown toadvantage and generally identified by the numeral 10. It is to beunderstood that the transmission 10 may be mounted and carried by any ofa variety of commonly known frameworks (not shown). The transmission 10may be conveniently divided into a hydraulic torque converter 11 and acountergear 12.

Power from a suitable source (not shown) may be applied to a shaft 13journaled for rotation in the hydraulic torque converter 11. The shaft13 is provided, at its terminal and opposite the hydraulic assembly 11,with a pinion gear 14 in communication with the countergear assembly 12.In practice it has been found to be convenient to provide a commonlyknown clutch assembly 15 between the pinion gear 14 and the hydraulicassembly 11. The shaft 13, in communication with the hydraulic assembly11, is journaled for rotation in a counter-gear housing 16. The shaft 13is journaled for rotation in a drive means communicating power 17 fromthe hydraulic assembly II to the countergear assembly 12. The meanscommunicating power 17 may include a sleeved driving sprocket 18, achain 19, and a commonly known over-riding clutch sprocket assembly 20suitably fastened to countergear shaft 21 of the gear assembly 12.Hence, it is to be understood that the shaft 13 is journaled forrotation in the sleeved driving sprocket 18. A brake (not shown) may bemounted on the shaft 21 between the overriding clutch sprocket 20 and agearset 22, giving additional selective control means in operation ashereinafter later described.

Referring now to theFIG. 3 showing to advantage the hydraulic torqueconverter assembly II in a side crosssection elevational view, theassembly 11 comprises a cylindrical housing 23, a drum assembly 24, arotor assembly 25, and a blade control means 26. It is to be understoodthat the interfaces between the respective assemblies, and between theassemblies and the housing, may be provided with suitable frictionreducing means, such as bushings, bearings, and the like, commonly knownin the art. a

The drum assembly 24 includes a pair of opposing sidewalls 27 and 28 andan upstanding intermediate wall 29 disposed between the respectivesidewalls 27 and 28. Hence, the drum assembly 24 is divided intochambers 27 and 28'. The drum assembly 24 is suitably fastened to theshaft 13 by the wall 27, and rotated within the housing 23 in responseto rotation of the shaft 13. The rotor assembly 25 is mounted within thedrum assembly 24, and includes a hollow shaft portion 30 journaled forthe rotation on the shaft 13. The sidewall 28 of the drum assembly 24 isjournaled for rotation on the shaft portion 30 of the rotor assembly 25.A collar 31 is provided on the sidewall of the housing 23 opposite thesleeved sprocket assembly 18 carried on the shaft portion 30. The collar31 includes an entranceway 32 in communication with a suitable source offluid under pressure. The shaft 13 is provided with a multiplicity oftranverse holes 33 operable to sequentially align with entranceway 32 inresponse to rotation of the shaft 13. A multiplicity of transverse exitholes 34 are distally disposed on the shaft 13 in alignment with theholes 33, the holes 35 provided on the shaft portion 30 of the rotorassembly 25, and exitways 36 provided in the blade control means 26hereinafter later described. A rectilinear conduit portion 37 isprovided in the shaft 13 between the respective holes 33 and 34. Fluidunder pressure may be conducted through the entranceway 32 in the collar31; through holes 33 in the shaft 13, when aligned with the entranceway32; through the conduit 37 and the holes 34 on the shaft 13; through theholes 35 on the shaft portion 30; and through exitways 36, when theholes 33, 34 and 35 and the entranceways 32 are in simultaneousalignment.

As set out above the drum assembly 24 is divided by the centrallydisposed wall 29 into chambers 27' and 28'. The cylindrical wall of thechamber 28 and the adjacent portions of the walls 28 and 29 are providedwith a plurality of inwardly projecting fins 38. It is to be understoodthat the chamber 28' is usually filled with viscous fluid, such as oil.As the drum assembly 24 rotates,

the fins 38 act on the fluid carried in the chamber 28' causingcentripetal motion of the fluid. The cylindrical wall of the chamber 27'is provided with a plurality of oil ports 39. The oil ports 39, providedin the cylindrical walls of the chamber 27', provide means communieatingthe chamber 27 with the interior of the housing 23 through whichlubricating coolants may thereby cause circulation to cool the torqueconverter 11.

The rotor assembly 25 is carried within the drum assembly 24. The rotorassembly 25 comprises a cylindrical shaft 30 and an upstanding enclosure40. As set out above, the rotor shaft 30 is journaled for rotation overthe shaft 13 and in the housing 23. The shaft 30 projects from thehousing 23 at the end opposite the collar 31. It is to this projectingshaft portion of the rotor shaft 30 that the sleeved sprocket 18 isfastened. The enclosure 40 is carried within the chamber 27 of the drumassembly 24.

The rotor enclosure 40 includes an upstanding wall 41 disposed on therotor shaft 30 distally from 'the sidewall 27 of the drum assembly 24.The rotor enclosure 40 also includes a pair of centrally distallydisposed upstanding walls 42 and 43. In relation to the upstanding wall29 of the drum assembly 24, the rotor wall 42 is disposed distallywithin the chamber 28'. Thus, the wall 42 appears as a rotating diskwithin the chamber 28',

as more clearly shown in the FIG. 4. A cylindrical wall 44 is fastenedabout the circumference of the walls 41, 42 and carries the wall 43.

The blade control means 26 is carried within the rotor enclosure 40.Referring now to the FIGS. 5, 6 and 7, the blade control meanss 26comprises a pair of substantially wedge-shaped blade pairs 45 and 46, asleeved sun gear 47, blade gears 48, and blades 49. The pair ofsubstantially wedge-shaped blades 45 are opposingly fastened at theirrespective widest ends to the cylindrical wall 44. The complimentarypair of wedgeshaped blades 46 are opposingly fastened at their narrowends to a sleeve-like carrier 50, as shown more clearly by the FIG. 7.It is to be understood that the narrow end of the blades 45 and the wideend of the blades 46 ride freely against the respective opposing carrier50 and wall 44. The carrier 50 is journaled for rotation on the shaft 30on its portion under the enclosure 40 and is journaled for rotation inthe wall 43. It is in the carrier 50 that the aforementioned exitway. 36is disposed. Between the walls 42 and 43 the sun gear 47 is fastened tothe corresponding terminal end of the carrier 50. The blade gears 48 aredisposed on the wall 42 in planetary gear fashion about the sun gear 47on axis 48'. Referring to the FIGS. 4 and 5, which show both sides ofthe wall 42, a multiplicity of rotor blades 49 are disposed about thecircumference of the wall 42. Each blade 49 is fastened to an axis 48'.The blades 49 may be rectangular plates which are disposed at rightangles to the rotor wall 42, and which pivot on their respective axismeans 48' at their ends closest the center of the shaft 30. Each axis 48is journaled for rotation in the wall 42, and provides the axis ofrotation for each blade gear 48 and each blade 49. In this embodimentthe blade gears 48 are quarter gears.

In operation, pressure is applied between the wedgeshaped blades 45 and46 resulting in a displacement of blades 46 with respect to blades 45and rotation of the carrier 50. The rotation of the carrier 50 and sungear 47 results in rotation of the blade gears 48 and the blades 49 to amaximum power transfer angle of that shown in solid lines of the FIG. 4.To retract the blades 49, pressure is reduced between the blades 45 and46. Fluid in the chamber 28' tends to force the blades 49 to an angle ofattack of less resistance and less power transfer, shown by the blade 49in broken lines in FIG. 4. The blade gears 48 drive the carrier 50 torotate in reverse and the blades 45 and 46 come closer together.

Referring now to the FIGS. 8, 9 and 10, a further embodiment of therotor assembly 25 and the blade control means 26 includes a plurality ofblades 51 which are substantially fan-shaped plates. Each blade pivotson a shaft 52 centrally disposed at the narrower terminal end of eachblade 51. The shafts 52 are journaled for rotation in a polygonallyshaped block 53 carried on the rotor shaft 30. The block 53 has apolygonal side for each of the blades 51. Each of the shafts 52 isprovided with a bevel gear 54 mounted at its respective terminalend ofeach shaft 52 closest the shaft 13 as shown more clearly in the FIG. 9.The sun gear 47 of the further embodiment is a beveled sun gear. Thefins 38 have a concave configuration on their respective inner terminaledges to conform distally to the convex outer edge of each of the blades51.

In operation, pressure is applied as set out above and the beveled sungear 47 rotates. The rotation of the sun gear 47 forces the bevel gears54 to rotate, thus changing the angle of attack of the blades 51. Theangle of maximum power transfer is at right angles to the drum sidewall28 as shown by the blades 51 in solid lines in FIG. 10. The angle ofattack of least power transfer is a blade parallel to the drum wall 28,shown in broken lines in FIG. 10. Referring to FIG. 8, to reduce power,pressure between the blades 45 and 46 is reduced. Fluid in the chamber28' tends to act on the unsupported sides of the blades 5 1, thusrotating the blades 51 in the angle of attack of less resistance. It isto be understood that in both ofthe above embodiments there are aninfinite number of settings available through the blade control means26.

Referring again to the FIG. 1, the hydraulic torque converter 11 may beprovided with a countergear assembly 12 to provide higher and loweroutput speed ranges to the converter 11. The countergear'12 comprises acountergear shaft 21, a gearset 22, and a direct drive means 14. Thecountergear 21 is journaled for rotation in the aforementioned housing16. The countergear shaft 21 is driven by the afore-mentioned meanscommunicating power 17. The means 17 may be engaged and disengaged fromthe shaft 21 by a clutch 20. At one of the terminal ends of the shaft 21is suitably disposed the gearset 22. Thus, it may be seen that thecountergear assembly 12 is a torque power transmitting apparatus whichmay be analogous to a countergear of gear-type transmissions.

The gearset 22 is intended to change the direction of rotation of theoutput of the variable speed transmission 10, and may be geared inratios, which may increase or reduce output speed, as shown to advantagein the FIGS. 1 and 2. The gearset 22 is carried in a housing 55 andcomprises a sun gear 56, a plurality of gears 57, and a ring gear disk58. The sun gear 56 is fastened to the terminal end of the shaft 21. Theplurality of gears 57 are disposed on journaled shafts 59pm vided on oneof the interior sidewalls of the housing 55. The ring gear disk 58comprises a ring gear 60 fastened to a circular disk-like plate 61,which is in turn fastened at the disk center to a output shaft 62. Thering gear 60 is provided with suitable teeth and pitch on its innercircle to engage the gears 57. The countergear shaft 21 drives the sungear 56, which drives the gears 57 in an opposite direction of rotation,which drives the ring gear disk 58 and the output shaft 62 in the samedirection as the gears 57.

The direct drive 14' is operable to transmit power directly from thepower source to the gearset 22. The direct drive 14' comprises theaforementioned shaft 13, pinion 14 fastened to the terminal end of theshaft 13 and a clutch disposed between the pinion 14 and the torqueconverter 11. The pinion 14 engages teeth on the outer edge of the ringgear disk 58. The ring gear disk 58 projects through the terminal edgeof the housing 55 through an opening suitable to permit the ring geardisk 58 to engage the pinion 14. It may be seen that the structure ofthe gearset 22 may be analogized with a planetary gearset and adifferential gearset in that there are two power input shafts 13 and 21and a single output shaft 30, although the shafts 13 and 21arealternately engaged, and in that the gears 57 are disposed about thesun gear 56 and within the ring gear disk 58 in a manner analogous to aplanetary gearset.

In operation the countergear assembly 12 is engageable with the shaft 21to drive the gearset 22 by disengaging clutch 20 and engaging the clutch15 thus disengaging the pinion 14. Alternately, the direct drive 19maydrive the ring gear disk'60 by disengaging the clutch 15, thusdriving the pinion 14 on the shaft 13, and engaging the clutch 20 anddisengaging the shaft 19 from driving the gearset 22.

Having thus described in detail a preferred apparatus which embodies theconcepts and principles of the invention and which accomplishes thevarious objects, purposes and aims thereof, it is to be appreciated andwill be apparent to those skilled in the art that many physical changescould be made in the apparatus without altering the inventive conceptsand principles embodied therein. Hence, it is intended that the scope ofthe invention be limited only to the extent indicated i the appendedclaims.

I claim:

1. A variable speed transmission comprising: a drum assembly, connectedto an input shaft from a suitable torque power source, having acylindrical chamber carrying fluid, said chamber having fins atintervals on its inner cylindrical wall; a rotor connected to an outputshaft, carried in said drum assembly, having a plate per- ,pendicularlydisposed to said rotor output shaft, and

having a plurality of selectively movable blades disposed at intervalsdistally from the circumference of said rotor plate; blade control meanscarried in a cylindrical enclosure on said rotor and including a pair ofopposing wedge-shaped members having their widest ends fixedlydependently mounted to the interior terminal side of the cylindricalwall of said enclosure, a pair of opposing wedge-shaped members havingtheir narrowest ends dependently mounted to a sleeve-like carrier, saidsleeve-like carrier having a sun gear at one of its terminal ends toengage with a plurality of suitable quarter gears connected to saidblades; and a suitable pressure means for selectively forcing said pairsof wedge-shaped members apart and to selectively actuate said sun gearof said sleeve-like carrier.

2. The apparatus of Claim 1, including a countergear assembly,comprising: a countergear drive shaft connected to said output shaft ofsaid rotor; a gearset comprising a sun gear disposed at one of theterminal ends of said countergear drive shaft, a plurality of suitablydisposed gears each engageable with said sun gear, and a ring gearhaving suitably configured teeth on its inner wall operable to engagesaid gears, and suitably configured teeth on the outer terminal wall ofsaid ring gear, said ring gear being fixedly fastened to a diskconnected to a countergear output shaft; a direct drive pin ion fastenedto the terminal end of said input drive shaft operable to engage saidouter gear teeth of said ring gear; and clutch means on saidcountergear'drive shaft and on said pinion portion of said input driveshaft to selectively alternately engage said countergear or said pinion.

3. The apparatus of Claim 1, wherein said blades comprise rectangularplates pivotally mounted at one of their terminal ends to the shaft ofeach of said quarter gears.

4. The apparatus of Claim 1, wherein said blades are suitably carried ona suitably configure d polygonal ro tor, said blades mounted on shaftshaving at their end opposite said blades suitably configured bevel gearsengageable with a bevel sun gear.

I! i II! 1 l

1. A variable speed transmission comprising: a drum assembly, connectedto an input shaft from a suitable torque power source, having acylindrical chamber carrying fluid, said chamber having fins atintervals on its inner cylindrical wall; a rotor connected to an outputshaft, carried in said drum assembly, having a plate perpendicularlydisposed to said rotor output shaft, and having a plurality ofselectively movable blades disposed at intervals distally from thecircumference of said rotor plate; blade control means carried in acylindrical enclosure on said rotor and including a pair of opposingwedgeshaped members having their widest ends fixedly dependently mountedto the interior terminal side of the cylindrical wall of said enclosure,a pair of opposing wedge-shaped members having their narrowest endsdependently mounted to a sleeve-like carrier, said sleeve-like carrierhaving a sun gear at one of its terminal ends to engage with a pluralityof suitable quarter gears connected to said blades; and a suitablepressure means for selectively forcing said pairs of wedge-shapedmembers aparT and to selectively actuate said sun gear of saidsleeve-like carrier.
 2. The apparatus of Claim 1, including acountergear assembly, comprising: a countergear drive shaft connected tosaid output shaft of said rotor; a gearset comprising a sun geardisposed at one of the terminal ends of said countergear drive shaft, aplurality of suitably disposed gears each engageable with said sun gear,and a ring gear having suitably configured teeth on its inner walloperable to engage said gears, and suitably configured teeth on theouter terminal wall of said ring gear, said ring gear being fixedlyfastened to a disk connected to a countergear output shaft; a directdrive pinion fastened to the terminal end of said input drive shaftoperable to engage said outer gear teeth of said ring gear; and clutchmeans on said countergear drive shaft and on said pinion portion of saidinput drive shaft to selectively alternately engage said countergear orsaid pinion.
 3. The apparatus of Claim 1, wherein said blades compriserectangular plates pivotally mounted at one of their terminal ends tothe shaft of each of said quarter gears.
 4. The apparatus of Claim 1,wherein said blades are suitably carried on a suitably configuredpolygonal rotor, said blades mounted on shafts having at their endopposite said blades suitably configured bevel gears engageable with abevel sun gear.